Actuating device for web piercing pins of folder mechanism



Aug. 12, 1969 F. NEAL ET AL 3,460,823

ACTUATING DEVICE FOR was PIERCING PINS 0F FOLDER MECHANISM Filed April 13. 1967 2 Sheets-Sheet 1 INVENTORS FRANK NEAL ROBERT A. SNYDER BY Aug. 12, 1969 F. NEAL ET AL ACTUATING DEVICE FOR WF'BB PIERCING PINS OF FOLDER MECHANISM Filed April 13. 1967 mvsmons FRANK NEAL 2 Sheets-Sheet 2 ROBERT A. SNYDER B BY 7 ATT NEYS United States Patent 0 US. Cl. 270-77 9 Claims ABSTRACT OF THE DISCLOSURE A cam assembly for selectively actuating the web mounted circular cam, a cam follower for each pin assempiercing pin assemblies of a folding cylinder in straight and collect operation. The assembly includes a rotatably 'bly mounted for rotation with the folding cylinder and engaging with the circular cam at equally spaced distances thereabout, camming surfaces on the diametrically opposite sides of the cam for successively moving the cam followers to actuate the associated pin assemblies, and a power source for rotating the cam in the same direction as the cylinder at speed ratios of 3:2 and 3:4 relative to the speed of rotation of the cylinder to effect the desired straight or collect operation.

BACKGROUND OF THE INVENTION Field of the invention This invention relates to Web folding apparatus and more particularly to a 3-2 folding cylinder and the associated mechanism for operating the folding cylinder in either straight or collect operation.

Description-of the prior art In a typical folding cylinder as used, for example, with high speed newspaper presses, the newspaper, as it is fed to the folding cylinder in the form of a continuous web. is engaged by a set of pins on the folding cylinder and fed therearound to a pair of folding rolls. The web while on the folding cylinder is cut by a cutting cylinder into page sections and then fed between the folding rolls by means of folding blades provided on the folding cylinder. In a 3-2 folder mechanism, three separate pin assemblies are mounted internally of the folding cylinder for extension through openings located in the wall of the cylinder at equally spaced distances about its circumference. As the .folding blades are actuated to move a section of web into the bite of the folding rolls, the pins engaging that section are released.

When the folder is run in straight operation, every successive section of web is fed to the folding rolls immediately after being severed. Thus. three sections of web are fed to the folding rolls for each revolution of the folding cylinder. In some cases. it is desired to retain each section of web on the cylinder for one complete revolution so that each of these sections may be collected with another section and then folded off the cylinder. In order to operate a 3-2 folder in this manner, the web piercing pins holding the sections of web are actuated only after the second web section has been collected and the two sections together, fed past the folding rolls. With a 3-2 folder, collect operation means that each set of piercing pins will be actuated every other time they pass the release position rather than every time as when the folder is running in straight operation. Thus. in collect operation, three sections of web are folded into the folding rolls for every two revolutions of the folding cylinder.

3,460,823 Patented Aug. 12, 1969 ICC In presently constructed 3-2 folders of the type described above, it is conventional to provide a cam mechanism for operating the pin assemblies [in either straight or collect operation. For this purpose, each set of pins, i.e., each pin assembly, is mounted internally of the folding cylinder on a rotatable pin shaft and these pin shafts are each provided with a crank having a follower engaging with a cam as the cylinder, with the pin assemblies, rotates. The pin assemblies are mounted in the cylinder with their pins normally extending through the wall of the cylinder: and the cam is used to produce a rotation of the pin shafts first in one direction and then in the other, direction to momentarily retract the pins into the cylinder at the desired release point so as to permit removal of the web sections from the cylinder. Since the timing of the actuation of the pin assemblies must be changed depending on whether the folder mechanism is running in straight or collect operation, it is necessary to provide means for changing the cam mechanism to operate under each of these conditions.

In one conventional type of 3-2 folder. the cam mechanism used for actuating the pin assemblies includes two interchangeable cam plates. One of these plates is provided with a camming surface for effecting straight operation of the folder while the other is designed to effect collect operation. This type of actuating mechanism has certain disadvantages. For example, the individual cam plates are usually constructed to be removed from the folder mechanism when not in use. Thus, they are sub ject to becoming damaged or misplaced. In addition, when it is desired to change from one type of operation to the other, the changing of the cam plates requires precise resetting of the newly positioned plate before the folder is restarted. This is necessary in order to assure that the cam plate will cause proper actuation of the pin assemblies in timed relation to the actuation of the cutting cylinder and folder blade assembly.

In another 3-2 folder construction, the cam mechanism for actuating the pin assemblies comprises a cam plate which is mounted for rotation with the folding cylinder and against which the follower for each pin assembly engages. This cam plate is provided with a specified camming surface which causes the proper actuation of the pin assemblies in both straight and collect operation. When the folder is set for straight operation, the design of the camming surface of the cam plate. is

such as to require that the cam plate be held stationary with respect to the cylinder as the cylinder rotates. In collect operation, on the other hand, the cam is rotated with the cylinder at a predetermined speed causing actuation of the pin assemblies every other time they pass the release point in their rotation with the cylinder. In order to reduce friction and wearing of the followers of the pin assemblies as theyengage the camming surface of the cam plate, each of the followers is rotatably mounted on its associated pin shaft to produce a rolling engagement with the cam plate.

In a high speed folder mechanism, the speed of rotation of the folding cylinder is typically 400 revolutions per minute. Accordingly, the pin assemblies, mounted to the cylinder. and each of their followers also rotate about; the axis of the cylinder at this same speed. In a folder mechanism having a cam plate which is held stationary during straight operation. this means that the individual followers engaging against the camming surface of the plate will rotate about the axis of the cylinder at 400 revolutions per minute and about their ownaxes at a speed greatly in excess of 400 revolutions per minute. This high speed of rotation of the followers causes wearing of the followers, which, in turn, produces a loose engagement with the cam; and as a result, decreases the accuracy of pin actuation. If this wearing becomes considcrable, the pins may not retract to release the section of Web at the precise moment when the folding blades of the cylinder are being actuated, The pin retraction may be either premature or retarded. Where the pins release the web section prematurely and the web section has not yet come under the control of the folding blades, the section of web can become fouled. When, on the other hand, the pins are late in retracting, this can cause tearing of the web section as the folding blades push the sec tion into the folding rolls. Even slight error may cause difliculties in holding a paper section to the cylinder as such error may result in a bouncing movement being imparted to the pins which could result in loss of one or more pages of a section from the outer periphery of the cylinder.

SUMMARY OF THE INVENTION In accordance with the teachings of the present invention, an improved cam mechanism is provided for selectively actuating the pin assemblies in either straight or collect operation. In applicants construction, a cam plate is mounted for rotation about the axis of the cylinder and is driven through gearing in the same direction as the cylinder for both straight and collect operation. The cam plate is provided with a circular track into which three rotatable cam followers are received. These followers are connected to the pin shafts of the pin assemblies and are spaced from each other in the cam track by equal distances about the circumference of the track. The cam track, in turn, is provided with two radially displaced camming surfaces on its diametrically opposite sides; and each of these surfaces cause each of the cam followers to shift radially as they come ito engagement therewith. This movement of a cam follower causes its associated pin shaft to oscillate about its own axis to effect a momentary retraction of the pins fixed to that shaft and a releasing of the web section held thereby.

With this construction, the pin assemblies may be actuated in eiither straight or collect operation by controlling the speed ratio between the cam and the folding cylinder. With the folding cylinder rotating at 400 revolutions per minute, straight operation is produced by rotating the cam plate at 600 revolutions per minute or at a speed ratio of 3:2. This speed ratio causes engagement between one of the radially displaced camming surfaces of the cam track with each cam follower each time the associated pin assembly passes the designated release point. For collect operation, the speed ratio between the cam plate and folding cylinder is changed from 3:2 to 3:4; and in accordance with the teachings of the present invention, this is simply roduced by changing the gear drive to the cam plate. With a 3:4 speed ratio, engagement between one of the camming surfaces of the cam track and each cam follower occurs only every other time the associated pin assembly passes the release point in its rotation with the folding cylinder.

With the construction of the present invention, the cam followers are thus caused to rotate at only 200 revolutions per minute about the axis of the cylinder for straight operation and only 100 revolutions per minute about the axis of the cylinder for collect operation. Accordingly, the life of the followers is greatly increased over the life of the followers in conventional folders where follower rotational speeds up to 400 revolutions per minute about the axis of the cylinder are encountered. In addition, the changing from one type of operation to the other requires only a simple changing of the gear ratio of the drive for the cam plate and no replacement or adjustment of the cam mechanism. Since there is no replacement of a cam mechanism, wear of the cam lobes and recesses will be even since they are rotating about the cylinder axis continuously. A still further advantage of the construction according to the invention is that total wear of the cam lobes will be reduced as wear is divided between two lobes instead of one as would be the case if a. cam mechanism were replaced or held stationary.

Applicants pin actuating mechanism is also constructed so that it may be disconnected from the power drive used for rotation of the cam. The cam may therefore be manually rotated to actuate the pin assemblies when the folder mechanism is shut down. This is advantageous in that it permits retraction of the sets of pins when it is desired to replace the rubber cutting blocks on the folding cylinder. These cutting blocks, which are provided for cooperating with the cutting cylinder, are disposed immediately adjacent each of the pin assemblies; and by being able to retract the pins, removal and replacement of these blocks is made easier and there is less chance of causing damage to the pins or injury to ones hands.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a cross-sectional view of the folding cylinder showing its mounting relative to the cutting cylinder and folding rolls of the folder mechanism;

FIG. 2 is a partial cross-sectional view of the folding cylinder showing the actuating mechanism for the pin assemblies; and

FIG. 3 is a schematic view of the actuating mechanism shown in FIG. 2.

DESCRIPTION OF THE PREFERRED EMBODIMENT With. reference to FIG. 1, the folder mechanism is shown as generally comprising a folding cylinder 1, an associated cutting cylinder 2 and folding rolls 3. The folding cylinder is provided with three sets of Web piercing pin assemblies 4 and a rotating folding blade assembly 5 mounted internally thereof. The web piercing pins 6 of the pin assemblies are mounted in a position normally eX- tending through openings 7 in the Wall of the folding cylinder. Upon rotation of the cylinder in a clockwise direction as viewed in FIG. I, the pins of each of the pin assemblies pierce through the web 8 being fed to the cylinder at spaced locations along its length; and as the web is fed around the folding cylinder, it is cut into web sections 9 by the knife assemblies 10 of the cutting cylinder 2. The cutting cylinder is driven in timed relationship to the folding cylinder to effect a cutting of the web in front of each set of piercing pins and rubber cutting blocks 11 are provided on the folding cylinder for cooperating with the knife assemblies.

As the folding cylinder rotates, each web section is brought into overlying position with respect to the folding rolls 3; and as a web section becomes centered over these rolls, one of the folder blades 12 of the folder blade assembly 5 is actuated to fold the web section into the nip of the folding rolls 3. At this time, the set of piercing pins holding the forward end of this web section is moved to a retracted position in the cylinder and thereby release this section from the folding cylinder. Depending on whether the folder is to be operated in straight or collect operation, the actuation of the pin assemblies and folding blade assembly will be controlled to fold off every Web section as it ini ially passes over the folding rolls or to retain these sections on the cylinder until they have been collected.

In accordance with the teachings of the present invention, the actuation of each pin assembly is controlled by a cam assembly generally designated at 13 in FIG. 2. This cam assembly is mounted for rotation about the longitudinal axis of the folding cylinder on an axially extending support member 14. The cam assembly includes a cam plate 15 mounted on the support member 14 by way of suitable bearings 16 wherein the plate may be rotated relative to the cylinder.

For operatively connecting the cam assembly to each set of pin elements, each set of pin elements is secured, by Way of a linkage 17, to a crank 18. Each crank is, in turn, fixed to a pin shaft 19 which is rotatably mounted in the interior of the cylinder by Way of the bearing supports 20 and each pin shaft is provided with a follower assembly which is adapted to ride in a cam track 21 formed in the cam plate. Each of the follower assemblies of the pin assemblies are fixed by a crank member 22 to one end of each of the pin shafts with each of these cranks extending radially of the longitudinal axis of its associated shaft so that arcuate movement of the followers about the pin shafts will produce rotation of the pin shafts.

As the folding cylinder rotates, each of the pin assemblies rotate with the cylinder about the latters longitudinal axis with each of the pin elements in its normally extending position; but as a pin assembly passes the pin release position designated A in the drawings, the pin elements thereof are momentarily caused to retract to release the web section for the subsequent folding operation by momentary oscillation of the pin shaft about its longitudinal axis. This latter movement is controlled by the shape of the cam track 21 of the cam plate cooperating with follower assemblies carried by each of the pin assemblies and by the relative speeds of rotation of the cam assembly and the folding cylinder.

To maintain an accurate control of each cam follower assembly in the cam track, the followers include a pair of rollers 24 and 25 and the track is constructed with axially spaced inner and outer surfaces 26 and 27 against which the rollers engage, the roller 24 against the inner surface 26 and the roller 25 against the outer surface 27. With this construction, the accurate control of each cam follower assembly is assured since the opposed surfaces of the cam track are always in engagement with opposite sides of the follower assemblies.

In FIG. 3 of the drawings, the separate pin assemblies and their associated structure are, for purposes of description, distinguished from each other by the letters a, b and c.

As shown in FIG. 3, the cam track 21 along its outer surfaces is provided with two cam lobes 28 and 29 positioned on the diametrically opposite sides of the cam track. These cam lobes are radially displaced with respect to the remaining portion of the cam track and cooperate with opposed recesses 30 and 31 on the inner surfaces of the cam track. Both of these recesses 30 and 31 have a shape complementary to the rollers of each of the follower assemblies whereby engagement of any one of the follower assemblies with either one of the cam lobes will cause such assembly to move smoothly into the opposed recess. As this occurs, the associated crank member 22 will be caused to move in an arcuate path about the axis of the associated pin shaft and thus cause the momentary oscillation of such pin shaft. This oscillation of the pin shaft will be first in one direction to cause the pin elements on that shaft to retract and then in the other direction to cause them to move back to their normal extending position. Due to the limited extent of the cam lobes as measured in a direction along the center line of the cam track, the retraction of the pin elements will be momentary and of just a suflicient length of time to release the web sections thereby held.

In accordance with the teachings of the present invention, the cam assembly 13 is rotatably driven in the same direction as the folding cylinder 1 and at a predetermined speed ratio relative to the speed of rotation of the cylinder. When the straight operation of the folder mechanism is desired, the cam assembly is rotated at a 3 :2 ratio while when the collect operation is desired, the cam assembly s rotated at a 3:4 ratio. In FIG. 3, the pin assembly 4a is shown in its retracted release position as caused by the radial movement of the associated follower assembly 23a passing over the cam lobe 28. When the folder mechanism is run in straight operation to fold off three sections of web for each revolution of the cylinder, each of the follower assemblies, 23a, 23b and 23c must be inalignment with one of the cam lobes 28, 29 of the cam assembly each time the associated pin assembly passes the release position A.

If, for example, the folding cylinder is rotated at 400 revolutions per minute to effect straight operation, the

cam is rotated at 600 revolutions per minute. Thus, using angles of rotation, the folding cylinder will rotate 40 for a cam rotation of 60. Accordingly, with reference to FIG. 3, as the pin assembly 4b moves clockwise 120, to t the position of the pin assembly in, the cam assembly will move 180 bringing the cam lobe 29 and opposed recess 31 to the position of cam lobe 28 and recess 30. This will then cause a momentary retraction of the pin elements 6b of the pin assembly 412.

With this speed ratio, the next 120 of rotation of the folding cylinder will bring the pin assembly 40 into the position of pin assembly 4a and at the same time, the cam assembly will be rotated an additional 180 to bring the cam lobe 28 and recess 30 back into the position shown in FIG. 3 and thus cause actuation of the pin assembly 40. With this construction operated at the speed ratio of 3:2, it is seen that each time a pin assembly passes the pin release point A, one of the cam lobes 28, 29 will also be positioned in engagement with the associated follower assemblies and thus straight operation of the folding mechanism will be effected.

As the folding cylinder and cam assembly rotate relative to the other at the speed ratio of 3:2, the cam follower assemblies 23 being in engagement with the cam track will also be caused to rotate about their own shafts. Since, however, the folding cylinder is rotating at 400 revolutions per minute and the cam at 600 revolutions per minute, the effective speed of the follower rollers will be only 200 revolutions per minute about the axis of the cylinder. This is considerably less than both the speed of rotation of the cylinder and the cam and advantageously decreases the wearing of the follower rollers.

In collect operation of the folder mechanism, the speed ratio of the cam assembly to the folding cylinder is changed to 324-. Accordingly, with the cylinder rotating at 400 revolutions per minute, the cam assembly will rotate at 300 revolutions per minute and thus, for every 40 of rotation of the folding cylinder, the cam assembly will rotate 30. Starting with the position of the parts as shown in FIG. 3, a rotation of the folding cylinder through 120 in a clockwise direction to bring the pin assembly 4b into the pin release point will be accompanied by only of rotation of the cam assembly. Since no cam lobe is engaging any one of the cam followers at this point, no pin withdrawal will be effected. An additional 120 of rotation of the folding cylinder will, however, bring the pin assembly 4c to the pin withdrawal station A and by this time, the cam lobe 29 will also be in the withdrawal position having rotated an additional 90. In the collect operation, the rotation of each of the cam follower rollers about the axis of the cylinder will be the difference between the speed of rotation of the cylinder and that of the cam assembly or revolutions per minute. Thus, in collect operation, the cam followers are subjected to even less wear than in straight operation.

The drive for the cam assembly is run from the power source used to rotate the folding cylinder. As shown in FIG. 2, a drive shaft 32 is provided. This drive shaft is driven by a power source (not shown) through the gear assembly 33 at, for example 1200 revolutions per minute. The drive shaft includes a cylinder drive gear 34 meshing with the gear 35 mounted on one end of the folding cylinder. The size of these gears 34, 35 is such as to rotate the folding cylinder at the desired 400 revolutions per minute.

A helical drive gear 36 is also provided on the drive shaft 32 and mounted for movement therealong by the splined support 37. The helical drive gear 36 meshes with a helical driven gear 38 fixed to a first driven shaft 39. This first driven shaft also includes a first gear 40 and a second gear 41 spaced axially therealong. Rotation of the drive shaft causes rotation of the first driven shaft 39 through the helical gears 36, 38 and thus, causes rotation of the first and second gears 40 and 41.

Mounted for rotation about an axis parallel to the first driven shaft is a second driven shaft 42. On one end of this shaft 42 are third and fourth gears 43 and 44, respectively. These two gears are mounted on the shaft 42 for rotation therewith and for axial movement therealong from a first position shown in solid lines in FIG. 2 to a second position shown in dotted lines. In the first position, the gears 40 and 43 are in meshed engagement with each other while in the second position, the gears 41 and 44 are in meshed engagement with each other. For moving the gears 43, 44 between the first and second positions, a handle 45 is provided. This handle is pivotally mounted about the handle support member 46 for rotation between the solid line and the dotted line positions shown in FIG. 2.

To connect the gear drive to the cam assembly 13, a fifth gear 47 is mounted on the other end of the second driven shaft 42. This gear 47 meshes with a cam gear 48 fixed to the cam plate 15 of the cam assembly whereby rotation of the driven shaft 42 and the gear 47 causes rotation of the cam assembly. The solid line position of the gears shown in FIG. 2 effects straight operation of the folder while the dotted line position produces collect operation. The number of teeth on the gears 40 and 41 and on the associated gears 43 and 44 are related to each other to produce the desired 3:2 speed ratio of the cam in straight operation and the 3:4 speed ratio in collect operation.

As shown in FIG. 2, the left hand end of the second driven shaft 42 is provided with a squared end 49. Also, the axial spacing between the gears 40 and 41 is greater than the axial dimension of the gears 43 and 44. Thus, the gears 43, 44 can be moved to a third position between the gears 40, 41 to disconnect the drive to the cam assembly. When in this position, a suitable tool may be attached to the squared end 49 of the shaft 42 to rotate this shaft and thus the cam assembly 13. With this construction, any one of the pin assemblies may be retracted as desired and this is advantageous when, for example, it is necessary to replace the cutting blocks 11. These blocks are disposed quite close to the web piercing pins and by being able to retract the pins independently of any rotation of the folding cylinder, removal of the cutting blocks when the folder is shut down is facilitated and damage to the pins or injury to ones hands is avoided.

For purposes of setting the cam assembly in proper rotative position relative to the folding cylinder so that retraction of the pin assemblies will be effected at the release station A, both the cam assembly and folding cylinder are provided with suitable timing marks (not shown). Alignment of these timing marks assures proper timing of the pin actuation and is made upon initial assembly of the folder mechanism. In addition, these marks are used to reset the cam any time the pin assemblies are manually actuated, as for example, when the cutting blocks are replaced.

During running of the folding cylinder, it is sometimes necessary to effect a fine adjustment of the point of retraction of the pin assemblies. For purposes of permitting this fine adjustment, an adjusting mechanism 50 is provided at the end of the drive shaft 32. This adjusting mechanism includes an adjusting screw 51 rotatably mounted in the folder support structure 52 whereby rotation of the screw 51 causes axial movement of the support 37 and helical drive gear 36 along the drive shaft. Such movement of the helical drive gear in turn causes rotation of the helical driven gear 38 and this rotation is effected independently of the rotation of the drive shaft. Accordingly, the relative rotational position of the cam assembly 13 with the folding cylinder is variable independently of the drive and therefore, the exact point of the pin withdrawal of the pin assemblies may be accurately controlled.

The above description of the present invention has been made with respect to the presently preferred embodiment; however, it is to be understood that various changes may be made thereto without departing from the scope of the invention as set forth in the following claims.

We claim:

1. In a web folder mechanism having a folding cylinder, means for rotating said cylinder about the longitudinal axis thereof at a predetermined speed, three sets of web piercing pins mounted internally of the cylinder for rotation therewith with each set of pins normally extending through openings in the cylindrical wall of the cylinder at spaced distances about its circumference for holding a section of web thereon, a pin shaft for each set of pins rotatably mounted internally of the cylinder and extending longitudinally of the longitudinal axis of the cylinder, and means connecting the pins of each set to its associated pin shaft whereby rotation of said pin shafts about their own axes in one direction causes retraction of said pins from their normal position into said cylinder to release said section of web and rotation thereof in the opposite direction causes extension of said pins to their normal position, the improvement comprising:

(a) cam follower means mounted in a common plane on each of said pin shafts at a location laterally offset from the longitudinal axis thereof for rotation with said pin shafts about the longitudinal axis of said cylinder as said cylinder rotates and with each of said follower means being mounted for rotation about the longitudinal axis of its associated pin shaft;

(b) cam means mounted in said plane for rotation in the same direction as said cylinder about an axis extending perpendicular to said plane centrally of said follower means and in engagement therewith, said cam means including two radially displaced camming surfaces on the diametrically opposite sides thereof for successively momentarily moving each of said cam follower means as it engages with one of said camming surfaces in an arcuate path about the associated pin shaft to cause said associated pin shaft to rotate in said one direction to momentarily retract the pins thereon from their normal extending position; and

(c) means for rotating said cam means in the same direction as said cylinder selectively at a speed ratio of 3:2 and 3:4 relative to the speed of rotation of said cylinder.

2. In a web folder mechanism having a folding cylinder, means for rotating said cylinder about the longitudinal axis thereof at a predetermined speed, three sets of web piercing pins mounted internally of the cylinder for rota tion therewith with each set of pins normally extending through openings in the cylindrical wall of the cylinder at spaced distances about its circumference for holding a section of web thereon, a pin shaft for each set of pins rotatably mounted internally of the cylinder and extending longitudinally of the longitudinal axis of the cylinder, and means connecting the pins of each set to its associated pin shaft whereby rotation of said pin shafts about their own axes in one direction causes retraction of said pins from their normal position into said cylinder to release said section of web and rotation thereof in the opposite direction causes extension of said pins to their normal position, the improvement comprising:

(a) a crank connected to one end of each of said pin shafts for rotation therewith, each of said cranks extending radially relative to the longitudinal axis of its associated pin shaft;

(b) a cam follower mounted on the extending end of each of said cranks;

(c) cam means having a circular cam track thereon for rotation about the longitudinal axis of said cylinder in engagement with said cam followers and having two radially displaced camming surfaces on the diametrically opposite sides thereof for successively momentarily moving each of said followers as it engages one of said camming surfaces in an arcuate path about the associated pin shaft to cause said associated pin shaft to rotate in said one direc- 9. tion to momentarily retract the pins thereon from their normal extending position; and

(d) means for rotating said cam means in the same direction as said cylinder selectively at a speed ratio of 3:2 and 3:4 relative to the speed of rotation of said cylinder.

3. A folder mechanism according to claim 2 wherein:

(a) said cam means comprises a rotatable plate;

(b) said cam track is defined by a groove in one side of said plate for receiving said cam followers, said groove having a first surface facing radially outwardly of said plate and engaging said followers on one side thereof and a second complementary shaped surface opposing said first surface and engaging said followers on the other side thereof;

() each of said cam followers comprise rollers mounted on its associated crank for rotation about an axis parallel to the axis of rotation of said rotatable plate;

(d) each of the diametrically opposed camming surfaces of said cam track comprises:

(1) a cam lobe on one of said first and second surfaces of said groove extending into said track, and

(2) a radially opposed recess in the other of said surfaces, said recess having a shape complementary to the shape of said cam follower rollers for receiving same as said rollers engage against said lobe.

4. In a web folder mechanism according to claim 2 wherein said means for rotating said cam means includes:

(a) a drive shaft;

(b) a first driven shaft mounted for rotation about an axis parallel to the axis of rotation of said drive shaft;

(c) first gear means connecting said drive shaft to said cylinder and to said first driven shaft; said first gear means including:

(1) a helical drive gear mounted on said drive shaft for rotation therewith and for axial movement therealong, and

(2) a helical driven gear fixed to said first driven shaft in operative engagement with said helical drive gear;

(d) means connecting said helical driven gear to said cam means for effecting said rotation thereof; and

(e) means for changing the axial position of said helical drive gear on said drive shaft while said drive shaft is rotating to rotate said helical driven gear independently of its rotation as caused by rotation of said drive shaft.

5. In a web folder mechanism according to claim 4 wherein said means connecting the helical driven gear to the cam means includes:

(a) a first gear fixed to said first driven shaft for rotation therewith;

(b) a second gear fixed to said first driven shaft for rotation therewith, said second gear being spaced axially from said first gear;

(c) a second driven shaft mounted for rotation about an axis parallel to the axis of rotation of said first driven shaft;

(d) second gear means connected to said second driven shaft and operatively connected to said cam means for effecting rotation thereof, said second gear means being mounted on said second driven shaft for rotation therewith and for axial movement therealong from a first position in driven engagement with said first gear to a second position in driven engagement with said second gear, the number of teeth on said first and second gears being related to each other and to the number of teeth on said second gear means where-by engagement between said first gear and said second gear means drives the cam means at said 3:2 ratio relative to said second gear and said second gear means drives the cam means at said 3:4 ratio relative ot the rotation of said cylinder; and (e) means for moving said second gear rneans between said first and second positions. 6. In a web folder mechanism according to claim 2 wherein said means for rotating said cam means includes:

(a) a drive shaft;

(b) a first driven shaft mounted for rotation about an axis parallel to the axis of rotation of said drive shaft;

(c) first gear means connecting said drive shaft to said cylinder and to said first driven shaft;

(d) a first gear fixed to said first driven shaft for rotation therewith;

(e) a second gear fixed to said first driven shaft for rotation therewith, said second gear being spaced axially from said first gear;

(f) a second driven shaft mounted for rotation about an axis parallel to the axis of rotation of said first driven shaft;

(g) second gear means connected to said second driven shaft and operatively connected to said cam means for effecting rotation thereof, said second gear means being mounted on said second driven shaft for rotation therewith and for axial movement there along from a first position in driven engagement with said first gear to a second position in driven engagement with said second gear, the number of teeth on said first and second gears: being related to each other and to the number of teeth on said second gear means whereby engagement between said first gear and said second gear means drives the cam means at said 3:2 ratio relative to the rotation of said cylinder and engagement between said second gear and said second gear means drives the cam means at said 3:4 ratio relative to the rotation of said cylinder; and

(h) means for moving said second gear means between said first and second posiitons.

'7. In a web folder according to claim 6 wherein:

(a) said second gear means includes:

(1) a third gear mounted on said second driven shaft for rotation therewith and for axial movement therealong,

(2) a fourth gear mounted on said second driven shaft for rotation therewith and for axial movement therealong with said third gear,

(3) a fifth gear mounted on said second driven shaft for rotation therewith;

('b) said means for rotating said cam further includes:

(1) a sixth gear connected to said cam means for rotation therewith about the axis of rotation of said cam means and in driven engagement with said fifth gear; and

(c) said means for moving said second gear means includes a manually operable handle for moving said third and fourth gears from said first position in which said third gear is in driven engagement with said first gear and said fourth gear is located in a third position intermediate said first and second gears and out of engagement therewith to said second position in which said fourth gear is in driven engagement with said second gear and said third gear is in said third position.

8. A folder mechanism according to claim 6 wherein:

(a) said first gear and second gear on the first driven shaft are spaced axially from each other by a predetermined dimension; and

(b) the second gear means on said second driven shaft adapted to engage with either of said first or second 1 1 1 2 gears has an axial dimension less than said prede- References Cited termined dimension whereby it may be moved to a UNITED STATES PATENTS third position intermediate said first and second gears to disconnect the drive to said cam m n 313i? g i 33%;? .a s 9. A folder mechanism according to claim 8 wher in 5 1,829,243 10/1931 Smith X said improvement further comprises:

(a) independent actuating means connected to said EU EN RCAPOZIOPrimary Examiner second driven shaft for rotating said second driven V WILLIAMS Assistant Examiner shaft when the second gear means thereon are 10- i cated in said third position whereby said cam means 10 US. Cl. X.R. may be rotated independently of said drive shaft. 7070, 47

CERTIFICATE OF CORRECTION Patent No. 3,460,823 Dated Auqust 112i 1969 Inventor(s) F. Neal et a1 1 1 It is certified that error appears'flin the above-identified patent and that said Letters Patent are hereby corrected as shown below:

In the Abstract of the Disclosure, of the patent deed, line 14, "mounted. circular cam, a cam follower for each pin assem" should be line 17.

line 33 "ito" should read --into-- Column 3,

' 'eiither" should read :-either Column 3, line 39 Coluinn 10, line 3 4 "0t" should read --to" Column 10 line 42 "posiitons" should read -positions- SIGNED AND SEALED APR 2 81970 SEAL,

.At teat:

Atteating Officer 5810118? 01 1 

